Fluid-actuated rotary machine



Dec. 15. 1925- F. A. JIMERSON I FLUID ACTUATED RorARY/uAcaINE.

Filed may 9, 1925 INVENTOR flancisjlrfzme 0 50a,.

HIS ATT EY Patented Dec. 15, 1925.

UNITED STATES PATENT OFFICE.

FRANCIS A. JIMERSON, 0F ATHENS, PENNSYLVANIA, ASSIGNOR T0 INGERSOLL-RAND COMPANY, OF JERSEY CITY, NEW JERSEY, A CORYORATION OF NEW JERSEY.

FLUID-ACTUATED ROTARY MACHINE.

Application filed. May 9, 1925.

To all whom it may concem:

Be it known that I, FRANCIS A. J IMERSON, a citizen of the United States, and a resident of Athens, in the county of Bradford and State of Pennsylvania, have invented a certain Fluid-Actuated Rotary Machine, of which the following is a specification, accompanied by drawings.

This invention relates to fluid actuated rotary machines and tools, such as hoists, drills, and the like, but more particularly to such a machine which may be reversible and is operated by a motor having a plurality of cylinders provided with pistons connected to a common crank for imparting rotation to the crank shaft from which power is to be taken for the operative part to be actuated.

The objects of the invention are to increase the efliciency of the machine both on direct and reverse rotation, enable the advantages and economies of an efiicient cut off for the pressure fluid in the working cylinders to be utilized, and permit the use of an auxiliary exhaust in addition to the main exhaust, both on direct and reverse rotation, so that substantially the same power and economy are obtained in either direction of rotation.

The invention is illustrated in one of its preferred forms in the accompanying drawings, in which- Figure 1 is a longitudinal sectional elevation partly broken away showing so much of afiuid actuated rotary drill as will serve to illustrate the invention, and

Figures 2 to 7 inclusive, are detail transverse sectional views through the crank and valve bushing on the line 22 of Figure 1 looking in the direction of the arrows, illustrating the cycle of operations.

Referring to the drawings, the case A is provided with an enlarged chamber B at its rearward portion within which the cylinders extend, of which there are three in the present instance, only two cylinders C and D being shown in Figure 1 owing to the longitudinal section on which the drawing is made, as will be understood. There may of course be any desired number of these cylinders arranged singly or in pairs, but three angularly disposed cylinders will be sufficient for purposes of illustration. The cylinders in this instance are single acting and are preferably remoy ably connected to the Serial No. 29,981..

case A in any suitable or desired manner as by means of cylinder cap screws (not shown). The pistons F reciprocating in the cylinders are provided with suitable con meeting rods Gr suitably connected to a common crank pin H on a longitudinally extendmg crank J operatively connected in this instance by gearing at the front end of the machine to drive the rotary drill bit K carried in the spindle L. The pinion E on the forward end of the crank J meshes with the gear O on the spindle L as shown for drivmg purposes.

The supply of pressure fluid to the machine is controlled by a rotatable handle sleeve P suitably connected as by the pin and slot connection P" to actuate the reversing valve Q, inside the handle body R connected to the case A as by means of the threaded sleeve S. Any suitable reversing valve Q, may be provided having ports S and T and a passage U for pressure iiuid whereby the passages V and TV in the case A may alternately be made supply or exhaust passages, according to the direction in which the motor is intended to rotate the crank J. In the position of the parts shown in Figure 1, the pressure fluid supply enters at the inlet X at the outer end of the handle body and passes to the machine through the passage V, while the main exhaust passes out through the constantly openmain e):- haust port 06 except as controlled by the valve portion of thecrank J. The details of the reversing valve Q form no part of the present invention but are reserved for other applications for patent, so that the valve will not be further described herein.

In accordance with this invention the machine is provided with a supplemental or auxiliary exhaust port Z communicating with the port Y and passage XV controlled by the reversing valve Q. The case A is formed with the reduced bore 5 in which is located the stationary valve bushing c having suitable ports and passages controlled by cooperating ports in the rotating crank J for distributing the pressure fluid to and from the cylinders both on direct and reverse rotation of the motor.

Combined supply and exhaust passages (Z connect the cylinders with the ports 6 in the bushing c and the crank J is formed with the peripheral longitudinal grooves or ports and g cooperating with and connecting the bushing ports e and the ports 71- and in the bushing, which register respectively with the passages V and IV in the casing as the crank rotates in either direction. An exhaust port k in the crank communicates with the hollow bore 0 of the crank leading to the port 72 at the forward end of the hushing which in turn con'inuinicates with the main atmospheric exhaust port .0. in the case, so that the exhaust port It in the crank affords a main exhaust from the cylinders in addition to the auxiliary exhaust through the case port Z. The operation of the machine in its fundamentals as far as the supply and main exhaust of the cylinders is concerned is substantially like that of the somewhat similar machine disclosed in U. S.

Patent No. 1,385,134, granted to me .luly 19,-

1921, but in addition and in order to make the machine substantially equally powerful and economical of pressure fluid both on direct and reverse rotation I have provided the auxiliary exhaust IV and the operation of the machine of the present invention is best illustrated both by reference to Figure 1 and to the cycle of operations illustrated in Figures 2 to 7 inclusive, which show six diderent positions of the valved crank J in considering one cylinder and revolution counter-clockwise as the machine is viewed from the back or left hand end in Figure 1. This may be considered as direct rotation of the motor, since the angularity of the valve portion of the crank with relation to the ports it controls is slightly different on reverse or clockwise rotation owing to the reversal of the direction of the flow of pres sure fluid, without however altering the cycle.

In the operation of the machine with the reversing throttle valve Q in the position indicated in Figure 1, for direct rotation, let it be assumed that the crank is rotating counter-clockwise as Figures 2 to 7 inclusive are viewed. Figure 2 corresponds to the actual monientary position of the parts in Figure l and is the admission position for the cyliir dcr C, which will be the only cylinder con sidered, since the operation is automatically the same for all the cylinders. Live air is supplied from the throttle through passage V in the case and passes through the bush ing port it and the groove or port f in the crank to the bushing port 6 and thence to the cylinder. Figure 2 shows the port 6 slightly open and pressure fluid just ready to enter from port.

In Figure 3, the crank has rotated through about 120 to a position to cut 05 cylinder C through its port 6, and one of the other two cylinders is starting to exhaust to the auxiliary exhaust Z through its port 6 while the other is receiving live pressure fluid through its port 6 as shown by the arrows, since one of these cylinder ports 6 then communicates by means of the port 9 with the bushing port and the passage ll with the auxiliary exhaust Z.

In Figure 4 the crank has rotated through about 150 to the position of main release at which point the port K: is about. to receive the exhaust from port 6 for cylinder C and permit said exhaust to pass through the bore 0 of the crank to the main exhaust port a in the case.

In Figure 5 the crank has rotated about 229 to the position of auxiliary compression showing the port a for cylinder C again closed and the port has slight lap before connecting with port a for cylinder C to open the auxiliary exhaust for said cylinder.

in Figure (3 the crank has rotated through about 2"l. to the position of auxiliary xhaust or release for cylinder C and the port 5/ is about to receive the exhaust and permit it to pass out through the auxiliary exhaust port Z.

In Figure 7 the crank has rotated about 355 to the position of con'ipression and the port y has passed beyond the port (2 for cylinder C so that said cylinder port 6 is closed, and a lap is provided between admission port 7' and port 0 which is the compression lap. These laps which are provided make the crank anglarity slightly different on re verse rotation so that the angles of crank rotation are not exactly the same as given above, but will be readily understood by those skilled in the art. I'Vhen the motor is reversed, the port f] becomes the live pres sure fluid supply port and the port 7 becomes the auxiliary exhaust port, while the port remains a main exhaust port and the cycle of operations is the same as described, with the same momentary positions of the parts having the same functions.

The crank angles heretofore are not to be taken as exact but approximate for purposes of illustration, although they produce efficient operation as given. The result of the cycle on direct rotation, starting from the position of admission, Figures 1 and 2, is admission for forward rotation through about 120 to cut oif Figure 3, then expansion for 30 to about 150 to the point of main release Figure 4-; the main release or exhaust closes at about 229 having continued through 79, and then auxiliary compression takes place for 2, until the auxiliary exhaust starts at 231 continuing to about 355, after which there is a period of compression of 5 before admission for the next stroke.

On reverse rotation, admission necessarily commences at a point 5 in the reverse di rection from the initial starting point for direct rotation and continues for 124 until cut off takes place at a point 129 from zero position, then expansion takes place for 2 and main release or exhaust commences at 131 and continues to 210, counting from zero, so that main exhaust on reverse rotae tion occurs through the same angle of 7 9 as on direct rotation; then the main exhaust closes at 210 reverse and auxiliary compression takes place for 30 until the auxiliary exhaust opens at 240 reverse, which continues for 125 until admission on reverse takes place again 5 beyond the zero point.

These various angles may be varied as desired Without departing from the spirit of the invention as defined in the appended claims and I am not to be understood as limiting the invention to the construction shown and described since those skilled in the art will be enabled to devise equivalent construction.

1. In a fluid actuated rotary machine, the combination of a case, a fluid actuated motor having a plurality of cylinders in said case, a longitudinally extending crank shaft connected to be driven by said motor, main and auxiliary exhaust ports in said case, a throttle for controlling the supply of pressure fluid and the auxiliary exhaust of the machine, cylinder distribution passages in the case, and distribution ports and passages in the crank shaft cooperating with said cylinder passages and with the main and auxiliary exhaust ports, whereby the main and auxiliary exhausts are brought into operation for each cylinder during the rotation of the crank.

2. In a fluid actuated rotary machine, the

combination of a case, a fluid actuated motor having a plurality of cylinders in said case, a longitudinally extending crank shaft connected to be driven by said motor, main and auxiliary exhaust ports in said case, a throttle for controlling the supply of pressure fluid and the auxiliary exhaust of the machine, a valve bushing in the case around the crank, cylinder distribution passages in the case and cooperating distribution ports and passages in both the valve bushing and crank shaft, whereby the main and auxiliary exhausts are brought into operation for each cylinder.

3. In a fluid actuated rotary machine, the combination of a case, a reversible fluid actuated motor having a plurality of radially arranged cylinders in said case, a longitudinally extending crank shaft connected to be driven by said motor, main and auxiliary exhaust ports in said case, a reversing throttle controlling the supply of pressure fluid and the said auxiliary exhaust of the machine, distribution passages in the case for the cylinders, and ports and passages in the crank shaft cooperating with the main pressure fluid supply, the cylinder distribution ports, and the main and auxiliary exhaust ports, whereby pressure fluid is supplied to the cylinders and also exhausted therefrom through both the main and auxiliary exhaust ports.

In testimony whereof I have signed this specification.

FRANCIS A. JIMERSON. 

